Hydraulic mechanism for transmission of power.



A. G. M. MICHELL & H. C. NEWTON.

HYDRAULIC MECHANISM FOR TRANSMISSION OF POWER.

APPLICATION FILED DEC-5. 1912.

Patented. June 1, 1915.

6 SHEETSSHEET I.

A. G. M. MICHELL &'H C. NEWTON.

HYDRAULIC MECHANISM FOR TRANSMISSION OF POWER.

APPLICATION FILED DEC-5, 1912.

Patented June 1, 1915.

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A". e. M. MIC HELL & H. c. NEWTON. HYDRAULIC MECHANISM FOR TRANSMISSIONOF POWER. APPLICATION FILED DEC.5,1912..

Patented J 11110 1, 1915.

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A. G. M. MICHELL & H. G. NEWTON. HYDRAULIC MECHANISM FOR TRANSMISSION-0FPOWER.

APPLICATION FILED DEC-5. 1912- a 2 H i HM m 2w m I? h e WN M W L WW A.G. M. MICHELL & H. C. NEWTON. HYDRAULIC MECHANISM FOR TRANSMISSION OFPOWER. APPLICATION FILED DEC-5, 1912. I I 1 1 312, Patented June 1,1915.

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.HYDRAULIC MECHANISM FOR TRANSMISSION OF ,POWER.

APPLICATION FILED DEC-5,1912- Patented June 1, 1915.

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m zzessesf ED STATES mire ANTHONY GEORGE MALDON- MICHELL, OF MELBOURNE,ANiD HENRY CLEMENT NEWTON, OF KEW, NEAR MEBBOUBNE, VICTORIA, AUSTRALIA.

HYDRAULIC MECHANISM FOR TRANSMISSION OF POWER.

To all whom it may concern:

Be it known that we, ANTHONY GEORGE MALDON MICHELL, a subject ofthe Kingof Great Britain, residing at No. 450 Collins street, Melbourne,Australia and HENRY CLEMENT NEWTON, a subject of the King 'of GreatBritain, residmg at The Cottage, Walmer street, Kew, near Melbourne,aforesaid,have invented a Hydraulic Mechanism for Transmission of Power,of which the following is a specification.

This invention relates to hydraulic mechanism for transmitting powerfrom a primary rotating shaft to one or more secondary shafts, in orderthat the latter may be driven at varying speeds, and in certain.

cases, with either direction of rotation, without correspondingvariation of the speed of the primary shaft, the apparatus hereinafterdescribed being intended more particularly for the propulsion 'of motorvehicles, road and railway locomotives and boats.

The transmission is effected, as in some mechanisms of the same classpreviously proposed, by means of abody of liquid cir culatedcontinuouslythroutgh centrifugalpump and turbine rotors, orming respectively thedrivingand driven elements of the apparatus. The special features of thepresent invention consist in the mode of combination and arrangement ofsuch pump and turbine elements and their casings, and in the specialmodes of construction of the turbine rotors and guide-vanes andauxiliary'parts of the apparatus as hereinafter set forth and claimed. a

The turbine-rotors employed beingof the inward-flow reaction class andthe ump rotors being of the usual centrifuga outward-flow type, they aresoarranged in combination that the fluid flows directly from aperipheral outlet of the pump to a closel adjacent peripheral inlet ofthe correspond ing turbine. For this purpose the casings, (which in mostcases are preferabl combined to form one common casing or'the wholeapparatus) are so formed as to "consist substantially of peripheralchambers of continuously increasing sectional area, hereinafter calledhelices or helical chambers,

surrounding the pump andturbine rotors respectively, the mouth of eachpump. helix bein arranged to discharge into the mouth of t e helix ofthe corresponding turbine.

Specification of Ilietters Patent.

in the State of Victoria, '11

' productive of loss ofenergy a section t Patented June 1, 1915.

I Application filed December 5, 1912. Serial No. 785,129,

The helices are so proportioned that the fluid loses as little aspossible of the high velocity with which it leaves the pump rotor,before delivery into the turbine rotor, all such reuction of velocitybeing, as is well known, The primary object of the double-helicalconstruction of easing just described is to enable a high velocity to bethus maintained and a highpump efiiciency thus realized. Such generalarrangement of helices is modified as shown in the accompanying drawingsaccordin as one or more'turbine rotors are supp ied from a single pumprotor, and according as the pump and turbine are required to haveparallel axes,.with the same or opposite directions of rotation innormal running, or to have their axes incline'd, or at right angles, toone another. 11 these drawings, dot-dash lines on' various figuresindicate the lines on which the sections illustrated are made, each linebein numbered in Roman numerals to correspon with the number of thesectional figure corresponding to such lin Fi res 1 to 5 arediagrammatic sections, showing the types of apparatus in which theinvention may be applied and the mode of circulation of the fluid; Fig.1 being anaxial section, and Fig. 2 a transverse secand 11 illustratethe ap lication of the invention to parallel sha ts; Figs. 6 and 7beingrespectively transverse and axial sections of one arrangement andFig. 8 being -.an axial section of another arrangement;

Fig. 9 a transverse section on line IXIX ofFig. 8; and Figs. 10 andlldetail sec- 100 tional views showing the operation of 'turbineguide-vanes. Figs. 12 to 18 illustrate the application of the inventionto a pair of coaxi'al secondar shafts at right angles to the primary shaFig. 12 being partly 105 a plan and artly a section in the commonhorizontal ane of the three shafts; Fig. 13

liiough the turbine axes at right angles to Fig. 12;,Figs. 14 and "15sections transverse to the turbine and pump shafts respectively; Figs.16 and 17 partial sections parallel to Fig. 14; and Fig. 18 an enlarged"rotation of the rotors, and straight arrows to indicate the'directionsof flow of the fluid.

In Figs. 1 and 2 the common casing 1, consists as hereinbefore describedof two helical chambers surrounding respectively the pump rotor 2 andturbine rotor 3 both rotating clockwise as shown in Fig. 2. The pumprotor 2 discharges the fluid tangentially out of the mouth of itsperipheral helix 4 and tangentially into the opposed mouth of thesymmetrically arranged turbine helix 5 from which it flows into theturbine guide-vanes v6 and turbine rotor 3. These parts are shown bydotted lines in Fig. 2, which is a section through thereturn-flowchamber 7 connecting the axial outlet 8 of the turbine rotor 3, with theaxial inlet or eye 9 of the pump rotor 2. In all cases the returnchambers, as well as the helical chambers themselves are made as shortand direct as possible, for the pur ose of diminishing frictional lossesin' the flu1d, which as hereinbefore explained is, for reasons ofefiiciency, circulatedat high velocity. For the same purpose ofshortening the paths of fluid flow and for other reasons explainedhereafter the helices 4 and 5 ma the whole periphery o the rotors 2 and3, but the fluid may be conducted from a portionof the'periphery ofrotor 2 to a corresponding portion of guide-vanes 6 by means ofaux1liary guide-blades 10. Alternatively such auxiliary guide-blades maybe employed in connectlon with one rotor only, the helix of the otherrotor being com lete, such arran ements being more fully escribed heremate r. In this and the other forms the helix 1s constructed with itssectional area at each pomt as nearly as possible proportional to theflow,-so that the velocity is uniform throughout.

In Fig. 3 the pump rotor 2, turbine 3 and guide-vanes 6 are constructedand arranged Figs. 1 and 2, except that the rotors are adapted to rotatein directions op osite to one another as shown by the curved arrows.W1th th1s object the helices 4 and 5 are so connected mouth to mouth asto form an S shaped figure, instead ofa C-shaped figure as1n Fig. 2. Thefluid is returned from the turblne to the pump, as. in Figs. 1 and 2,through the return chamber 7.

As will be evident, the mode of construction and operation of'theapparatus shown in Figs. 1, 2'and 3 may be applied without alteration ifthe planes of the turbines and pump rotors lie at an angle with oneanother, instead of coinciding as shown in those figures. In suchalternative arrangenot extend around substantially as described inconnection with ment which is more fully described hereinafter inconnection with Figs. 12 to 18, the.

"along a common'tang'ent line as in Figs. 1,

2 and ,3. In either case ,the flow into and out of the helices issubstantially tangential to the respective rotors, as stated above.

In the construction shown in Fig. 4, a compound turbine-rotor isemployed which consists of two parts or sections 3 and 3, used forforward and reverse driving respectively. According to the purpose towhich the mechanism is to be applied, the forward and reverse parts ofthe rotor may be mounted respectively on separate co-axial shafts 11 and11 extended out of the casing in both directions as shown and capable ofindependent rotation, or both parts of the rotor with those figures, butthe pump rotor is' made double with two axial inlets 9 and 9 on oppositesides, receiving respectively the circulated fluid throu h one or theother of the return chambers and 7, from one or the other of the outletsSand 8 of the res'pective parts 3 and 3.of the. turbine rotor accordinas one or the other part of the latter is %eing operated. A cylindricalsliding gate, not-shown in Fig. 4, arranged as hereinafter articularlydescribed in connection with igs. 12 to 18, surrounding and arrangedto'slide axially over the peripheries of the parts 3 and 3 of the rotor,or any equivalent known form of turbine control-gate, may be used toshut off the fluid from one or the other part of the turbine, leavinonly the one required in action, or from 0th parts of. the turbinetogether so .as to stop the whole of the driven mecha- 2. The reversepart 3 of the turbine and its guide-vanes '6 will beconstructedsubstantially as shown in Fig. 5,. the guide-vanes 6 being rccurved asshown so as to approximately reverse the direction of flow of the fluidentering the helix 5 as shown by the straight arrow,,before it entersthe periphcry of the part3 of the rotor, thus propelin connection withthe construction of pump 'ling the latter in an anticlockwise directionrotor 2 and common casing 1 shown in Fig. 2, in cases wherein it isdesired to drive a single secondary shaft in the opposite direction tothe primary shaft, instead of employing the mode of construction shownin Fig. 3 for this purpose.

Figs. 6 and 7 illustrate the application of the invention to the drivingof a number of spindles by means of a single pump element, Fig. 6 beinga transverse section analogous to Fig. 3 and Fig. 7 an axial sectionanalogous to Fig. 4.

The pump rotor 2, is situated at the center of the casing 1', which maybe divided transversely into two portions 1 and 1 as shown in Fig. 7.The fluid from the rotor 2 is discharged through each of the six partialhelical chambers 4, to one of the helical chambers 5, each of whichsurrounds one of the turbine elements.

Each of the turbine elements, like that shown in Fig. 4 ma be furnishedwith two peripheral series 0 fixed guide-vanes, one series 6 beingadapted for forward, and the other series 6 for reverse driving, theturbine rotor being also double and fitted with corresponding forwardand reverse blades, discharging at opposite ends of the rotor at 8 and8. By means of cylindrical slidinggates, (hereinafter described'inrelation to.

' Figs. 8-18), one or theother pair of vanes and blades may be opened tothe fluid, delivered by'the pump rotor 2, and the turbine rotor and itsspindle 11, 11, rotated in either direction at will. The fluiddischarged from the turbine at 8 or 8, is retur izied to the pump rotorby the passage 7 or Y -The mechanism shown in Figs. 6 and 7,

may be adapted to drive, as by means of multaneously, in ways wellunderstood, ex-' amples. being described below in connection with Figs.8 to 18.

Figs. 8, 9, 10 and 11 illustrate the a plication of the invention to thedriving 0 a pair of secondary shafts parallel .tothe primary shaft, thearrangement being devised particularly for useon motor vehicles and mechanically propelled boats.

The primary shaft 12 which carries the pump rotor 2 may be directlycoupled to the engine shaft as by a coupling 13- and may extend throughthe common casin pump and turbines, running in stu g boxes 14 and 15,and may have a journal 16 at the end opposite to the coupling 13, suchjour- 1 of thenal being carried by a bearing, not shown in the drawing,which may be rigidly secured to the casing 1. The pump rotor 2 as inFig. 4: is double, having two inlets 9 and 9 but in the present caseboth inlets are in operation simultaneously. The common casing 1 may,for. convenience, be divided into two halves by the joint 17 Fig. 9, inthe plane through the axes of the pump or primary shaft 12 and theturbine shafts 11, Fig. 8 being a section in the plane of this joint.

The casing 1, as set forth in connection with the diagrammatic Figs. v1to 5, comprises helical chambers surrounding the pump rotor 2 and theturbine guide-vanes 6 and 6. The pum rotor however, instead of having asingle elix, as in Figs. 1 to 5,

extending around substantially the whole. of its periphery, has two suchhelical chambers 4 and 4 each extending around substantends through thecasing 1 from'side to side,

leakage being prevented by the stuffing-boxes 18, 19. The forward andreverse parts 3 and 3* of the rotors, take opposite relative positionsin the two turbines, so that the fluid discharged from the turbines goesto both pump inlets 9, 9 and thus the pump rotor is hydraulicallybalanced, irrespective of which parts 3 or 3 of the rotors are in use.The turbine shafts 11 are. formed with journals 20, 21 at each end,running in bearings, not shown in the drawings, which may be rigidlysecured to the casing 1. Thrust bearings may be combined with one orboth of the bearings 20, 21.

For application to motor vehicles the turbine shafts 11 may be fittedwith universal couplings 22 connecting them to propeller shafts 23extending longitudinally rearward in the vehicle and each geared tonneof the rear, or driving, Wheels thereof by worm or bevel gearing, aswill be well understood, the usual differential gearing of such veh clesbeing'thus dispensed with. For application to boats, the couplings 22may be dispensed with or may be rigid, the propeller shafts 23 beingcarried through the stern of the boat and each fitted with a pro pelleras usual in twin screw boats.

The pump helices 4 and 4 may be supplemented by guide-blades 10 and10*,F1g. 9, as described in connection with Fig. 2. By inspection ofFig. 9, it will be apparent that the use of such guide blades enablesthe pump rotor 2, and turbine guide-vanes 6, 6,

to be brought closer together than would be the case if the helices 4,4, 5, were extended around the whole periphery of their respectiverotors, thus economizing space and weight.

The guide-vanes 6-and 6 of each turbine may be constructed in one rigidcylindrical.

- posite movements to the rods and hence to the gate cylinders G.

The rocking lever 26, and gates G being in the positions shown in Fig.8, which is the position for forward running of the turbine, the fluidis discharged from the pump rotor 2 in substantially equal quantitiesthrough the helices 4 and 4, mto the turbine helices 5, and thencethrough the vanes 6, into the parts 3 of the turbine rotors, rotatingthem in the clockwise direction, like the pump rotor itself, as will beclearly understood from the left hand portion of Fig. 9. When I thegates are in this position the inlets to the reverse parts 3of theturbine rotors are closed by the blank annuli 24 of the ates G, and theoutlet of the said parts 3 o the rotors are also at the same time whollyor substantially. closed by the blank annuli 24. By this means not onlyis the flow of fluid through the parts 3 of the rotors, which would actin opposition to the parts 3 thereof, prevented, but by covering theedges of the rotor-vanes of parts 3, any frictional resistance whichthey offer to the rotation.

.is minimized. From, the parts 3 of the rotors the fluid is dischargedby their outlets 8, in substantially equal quantities through the returnchambers 7, 7 tothe two inlets 9, 9, of the ump rotor 2, the returnchambers 7, 7,be1ng shut out of direct communication with the turbinehelices 5 by the. internal walls 28, 28 of such helices and-.by theannuli of the gates G.

When the lever 26 and gates G are moved to their other extreme positionsas shown for the right hand turbine of Figs. 8 and 9 in Fig. 10, theinlets of'the reverse turbine parts 3 of therotors are open to theturbine helices 5, through the reverse guidevanes 6. At the same timethe forward parts 3 of the rotors are closed by the blank annuli 24 andthe forward guide blades 6, and turbine outlets 8, by the internal walls28, but the reverse turbine outlets are open to the retur'n chambers 7and 7?. This is the position of the gates for reverse running at maximumpower. It will be readily understood that all degrees of power-less thanthe maxima for forward and reversed running may be obtained by -placingthe gates G in intermediate positions, between those above set forth, bymeans of the rocking lever 26, and also that, as-the blank annulus 24 ofthe gate, is of sufiicient axial length to cover the inlets of bothparts 3 and 3" of the rotors simultaneously, the circulation of fluidand rotation of both secondary shafts may be stopped by placing the gatein the proper position, while the pump and engine continue to run. Itwill also be understood, that the reverse parts 3 of the turbines may beused as brakes to oppose the forward motion of the vehicle or boat, byopening their inlets while the turbine shafts 11, and the vehicle orboat itself, are moving in the forward direction. In certain cases, asfor instance in the application of the invention to boats with twinpropeller shafts, the turbine gates may be controlled independently of.

one another by omitting the rocking lever 26 and separately operatingtherods 25,thus

enabling any re uired variation in the relative speeds and irections'ofrotation of the secondary shafts to be made. g

It is not essential that-the forward parts 3 of the turbines should beconstructedwith axial outlets 8, or the reverse parts of the turbineswith peripheral outlets, as the are respectively shown and abovedescribe but each of them may have-either an axial or peripheral outlet,as may be preferred for constructional or other reasons. y

The forms shown are however advantageous for application to roadvehicles in that the forward turbine, with an axial outlet,automatically opposes as its speed rises a back pressure to t e pressureproduced by the pump, and thus tends to. revent a dangerous speedb'eingobtained y the vehicle, while the reverse turbine with peripheral outletcan more readily be constructed to the fluid through the system, in thesame direction as in the normal operation of the gear, and thus todrivethe pump rotor 2 in the normal direction, assisting the engine ormaintaining the rotation of the pump independently of the engine. In theappllcation of this construction to motor vehicles, the reverse part 3of the rotor being put in action at high. vehicle-speeds on the downgrade, the engine may be kept axis of the one plane, assumed to behorizontal for fain action with the throttle valve closed, and withconsequent economy of fuel.

It is to be understood that the provision of forward and reverse bladesand guide vanes for each rotor shaft is not an essential feature of thearrangement described above in connection with Figs. 8 to 11, but thesame general mode of construction may be applied where the turbines arerequired to run in one direction only.

Both forward and reverse turbines may be fitted if desired with fixedoutlet guide blades as described hereafter in connection with Figs. 12to 18 by which the kinetic-energy of the water discharged from the turbines may be partially reconverted into pressure energy, in a mannerwell understood, and undue rotation of the water entering the pumpinletsprevented.

The apparatus shown in Figs. 8 to 11, may also be fitted with otherauxiliary apparatus described later in connection with Figs. 12 to 18.

Figs. 12 to 18 illustrate the application of the invention to a pair ofsecondary shafts having a common axis at right angles to the primaryshaft, all three being in cilitating the explanation. The arrangement ofapparatus shown and hereinafter described is designed particularly foruse in motor-vehicles being intended to be swung on the rearaxles of thevehicle, the axles being partly shown in the drawing and marked 30, 31,in a somewhat similar manner to the usual differential-box. The primaryshaft 12, which carries the pumprotor 2, may be coupled to a propellershaft of the usual kind flexibly coupled to the engine shaft, and run.in a stuffing box 32 to prevent leakage of the fluid. The common Icasing 1 of the pump and turbines is prefcrably divided as shown by a'joint 17 through the plane of the axes in the manner ghtreaiiivdescribed in connection with Figs.

0 D The pump rotor 2 is surrounded by two helical chambers 4, 4 formedin the casing 1, such chambers extending circumferentially around theperiphery of the rotor with sectional areas uniformly increasing fromtheir commencin points which are approximately diametrically oppositeone another and delivering respectively into the helical chambers 33,34, and thence alternatively into the forward guide-vanes 35, 36,

or reverse guide-vanes 35", 36", of the two turbine rotors 37,38.

The rotors 37, 38, are rigidly mounted respcctively on the shafts 39,-40 which are capable of independent rotation. and extend in oppositedirections out of the casing 1, through the stufling-boxes, 41 and 42,and

are carried respectively by bearings43, ar:

ranged in chambers 44, 45, of the casing 1,

or otherwise rigidly mounted therein.

The shafts 39, 40 ma each carry a pinion 46, whose teeth, pre crablyhelical, gear with a corresponding toothed wheel 47, mounted on thecorresponding road-axle 30 or 31, such gears running respectively ingear boxes 48,- 49, which may be divided into thrust bearings as 53,mounted in chambers,

orhousings 54, 55, provided or in the gear-boxes 48, 49.-

The outer ends of the axles 30, 31, are mounted in the usual manner inbearings, not shown in the drawings, rigidly attached to the tubes 50and 51, and by means of these bearings together with the inner bearings52, the casingl and its contained gearing are suspended in the samemanner as the ordinary differential gear-box from the axles.

The arrangement of gear-wheels as above described is adapted for use inthe common case of road vehicles having axles requiring a lower speedthan can conveniently be arranged for the turbine-shafts. When theconditions of use of the mechanism are such that this is not the casethe power may be applied directly by rigid or flexibly-coupledextensions of the turbine-shafts themselves. Alternatively the turbineshafts may be geared to the axles by chains, and in this case the casing1 may be rigidly connected to the chassis of the vehicle, instead ofbeing suspended on the axles 30 and 31 as'shown in the drawings andexplained above.

As above stated the turbine rotors 37, 38, and consequently theroad-axles 30, 31, are capable of independent rotation, thus enablingdifferential gearing of the kind usually fitted to such axles tobe'dispensed with. Tocarry out this object and to avoid the necessity ofproviding fixed bearings for the turbine shafts in the interior of thecasing -1, the spindle 39 of one of the turbine rotors 37 is extendedbeyond the rotor in the form of a long journal 39" and the other rotor38 is provided with a long boss 39, extending beyond the inner end ofthe spindle 40, such boss being bored to a working fit on the journal39. As already stated, the turbine rotors 37, 38, are rigidly mounted ontheir respective shafts 39 an 40, and

in the casing 1,

as will be explained hereinafter the fluid in Fig. 13 the end of theextension 39" of the I rotor 38, abuts on the boss/of the rotor 37.

vAlternatively the end of the extension 39? of the shaft 39 may abut onthe end of the shaft 40, the bosses of the rotors 37 and 38 having aclearance between them, instead of the bosses abutting and'the'shaftshaving a clearance as shown. In either case washers, not shown, may beinserted between the abutting ends of the shafts or bosses, in ways wellunderstood, to regulate the friction and distribute the wear.

In order to provide for the inward pressures or thrust exerted on thetwo rotors by the fluid pressures, as hereinafter .described, not beingprecisely equal, thrust washers 56 may be inserted between the drivingpinions 46, and faces 57 formed on the gear cases 48, 49, or betweenother suitable rotating and stationary parts, in

order to take the unbalanced thrust.

In cases which do not demand differential rotation of the two spindlesas above described, the turbine rotors 37, 38 may be rigidly mounted ona common spindle taking the place of the two spindles 39, 40. Thisarrangement may be adopted, for instance in the application of theinvention to railway locomotives, in which case the running wheels maybe mounted on the common shaft taking the place of the spindles 39, 40,and forming a running axle, mounted on a bogie of the locomotive, orotherwise.

As hereinbefore stated the two turbines 37 and 38 are respectivelysupplied by the pump rotor 2 with fluid through the helicalchambers 33and. 34, from the pump-chambers 4 and 4 respectivelv. The pumpchamher 4may extend around approximately one-halfof the perimeter of the pump asshown in Fig. 15 delivering at its mouth 58 into the mouth of theturbine helix 33. The chamber 4 commencing at 58 extendscircumferentially around the periphery of the rotor 2 to its mouth 59 atthe entrv of the turbine helix 34 into which it discharges. The fluiddischarged from the rotor 2 through the chamber 4 is supplemented bvthat discharged from the rotor between the mouth 59 of the chamber 4 andthe commencement of the chamber 4. In order to deliver this latterportion of the discharge without loss of its kinetic energy, guidevanes60, analogous to the guide-vanes 10 of Figs. 1 and 2, are arrangedbetween cheekplates 61, 62, and close y adjacent to the periphery of therotor 2, in the peripheral chamber 4*.

These guide vanes 60 are of recurved shape as shown, and reverse thetangential component of the fluid discharged from the correspondingportion of the rotor, so that such fluid is delivered in a substantiallyupward direction, as viewed in Figs. 15 and 17, to. flow at 59 into theturbine chamber 34 together with the fluid delivered from the chamber 4.,The cheek-plates 61, 62,

and their attached vanes, are preferably divided on the plane of thejoint 17 into an upper and lower portion respectively attached, as bystud-bolts 63, to the upper end lower portions of the case 1.

, In order to assist in attaining the desideratum hereinbefore stated,that the sectional area. of each helix should be proportional at eachpoint to the quantity of fluid flowing through it, ribs 64, 64 ,64", maybe formed on the interior of the walls of the casing 1 surrounding thepump rotor 2, whereby the effective area of the chambers 4, 4' 4", isincreased by the spaces between the rotor 2 and the case 1 extendinginwardly from the rotor-periphery to such ribs 64, 64", 64 Thepump-rotor 2 is fitted with blades 2, of the form usual in centrifugalpumps, producing at a given rotational speed a greater difference ofpressure between the outer and inner ends of such blades when the flowof fluid, as regulated by the turbine gates hereinafter described,

is small than when it is large. This prop- .rotor, as well vas'thekinetic energy as already stated, are maintained as far aspossiblewithout diminution up to the entry of the turbine guide-vanes.

The forward and reverse guide-vanes, 35, 35 and 36, 36 are preferablyformed in two stationary cylindrical sleeves 35, 36, surrounding therespective rotors 37, 38, and fixed in the-casing 1 so as to close theturbine helices 33 and 34 respectively, except at their mouths 58 and59, and at the openings into the turbine-guide vanes '35, 35 and 36,36". Fluid entering the vanes 35, 36 is delivered by them upon theforward turbine rotor blades 37, 38, respectively, from which it isdischarged, as shown, directly into the return chamber 65, while fluidentering the vanes 35, 36 is delivered upon the reverse rotor blades 3738*, from which it is discharged through the blades. 35, 36,respectively and thence likewise into the chamber 65. The blades 35, 36,are preferably formed in or attached to the .sleeves 35, 36.

The pressure of the fluid diminishes in its passage through theguide-vanes but remains greater at their inner ends than the ressure inthe return chamber 65, as is usual m reaction-turbines, so that there isa drop ends of the rotors 37 and 38 will he substantially the same asthat at the inner ends of lindrical surface of the external theguide-vanes, and that over the inner or adjacent ends substantially thesame as in forcing the two rotors in an axial direction toward oneanother.. The inlet 66 of the pumprotor 2 draws the fluid directly fromthe chamber 65, and the circulation is thus completed. a

Such pump inlet 66, is surrounded by the neck-ring 67 forminganjintegral part of the rotor 2, and rotating with minimum practicableclearance inslde a circular aperture between the pump chamber and thereturn chamber 65, being formed partly in the walls 68, 69, of thecasing 1 between the pumpchamber and the turbine helices 33, 34, asshown in Figs. 12, 16 and 17, and partly in portion of the casing 1 asshown in Fig. 14. v

On the opposite side, or back, of the pump rotor 2 the faucet-ring 70may be formed, surrounding with a similar clearance the exterior of thecylindrical stufiing-box 32, the h back of the rotor 2 being piercedwith suitable holes 71, tween the stufling-box 32 and the back of therotor 2 with that inthe front or suction side of the latter, and thusminimize thrust, in a well-known manner.

In order that the turbine-rotors 37, 38, and consequently the vehicleitself, may be drlven in eitherdirection or slowed or stopped at willwhile the engine and pump continue to run, turbine-gates 72, 73, areprovided. These consist of cylindrical sleeves, of uniform thickness,having preferably formedintegral therewith end webs, 74 and 75, and eachcarrying a pair of studs or gudgeons 76, 77. The end webs 74, 75, arebored to slide freely over the outer cythe tube 80, which surrounds theboss 39" of the rotor 38, being rigidly supported at the middle of itslength by the top and bottom webs 81*, 81", formed integral with orrigidly secured to the casing 1, and together forming a kind ofdiaphragm in the center of the return chamber 65. These webs 81, 81",may preferably be conneetedtothe outer by arms 81, 81", between them.tached to the tube '80, to limit the motion-of the webs 74, 75, of thegates 72, 73, in the outward direction,'their inwardmotion being limitedby the webs, BP-Iand 81".. The movement of these gates may be effectedas follows :-In the return chamber and wall of the casing 1respectively, having spaces transversely to the turbine axes, twospindles 84, 85, are fittedhipassing out from the chamher through stu ngboxes such as 86, fitted in the case 1, plugs the opposite ends ofbearings for them.

geared together by as 87 being provided at the spindles to serve as Thespindles 84, 85, are toothed'sectors 88, 89,

arms 91, 92, having to equalize the pressure be- I rotor-blades 37",38",

End pieces 82,83, may be'atpreferably external to the case, and one ofthem is fitted with a lever, 90, by means of which it can be rotated bya connectm rod from a pedal lever, not shown in the rawmgs, or othersuitable means.

Inside the return chamber 65, the spindles 84, 85, have respectivelysecured to them the double forked ends which engage respectlvel with thestuds 7 6, 77, on the gate-sleeves 7 2, 73. It will be seen thatwhen'the spindle 84 is partially rotated by the lever 90, clockwise asseen in Fig. 12 from the the'arm 91 will be rotated throu h the sameangle, and will displace the gate 2 from the posit1on in which it isshown toward the stop 82. At the same time the spindle 85 and arm 92will be rotated through an equal but opposite angle by the engagement ofthe sectors 88, 89, and the gate 73 will be displaced toward the stop83.

The gates 72, 73, which are made to slide easily inside the vanecylinders 35, 36, and to ave, the minimum practical running clearanceoutside the rotors 37, 38 (are each formed with two blank annularportions 72, 72" and 73, 73", respectively, connected by the annularseries of bars 78 78", 79", 79".

The blank annuli 72 73" are respectively of axial length sufficient tocover at once the openin s of both series of guide vanes 35*, 35" an36", 36"; the annuli 72", 73" are respectively of sufiicient length tocover the position therein shown,

outlets of the forward running rotors 37, 38; I

the annular bars 78", 7 9 are of equal length with the reverse vanes35", 36",'and the bars 78", 79", preferably of somewhat greater lengththan the last. when the gates 72, 73, are in the positions shown inFigs. 12 and 13, which are the positions for maximum turbine power inthe forward direction, being the extreme inward positions of the saidsleeves, the inlets of the forward outer ends of the blank annuli 72",73", so that they are open to receive the fluid from the forwardguide-vanes 35*, 36, respectively. At the same time the outlet ends ofthe blades 37*, 38 are free to discharge into the return chamber 65through the openings between the bars 7 8", 79", while the reverserotor-blades 37", 38", are wholly covered by are uncovered by the.

the blank annuli 72, 7 3", so that undue eddy resistance, on the edgesof these blades is avoided. When the gates 72, 73, are moved as abovedescribed by the-lever 90, through one-half of their possible travel,the blank annulus 72*, will cover, both the series of guide-vanes 35",35", and'the blank annulus 3" both the series of vanes 36", 36", and thefluid will be shut off from all the rotor vanes. When the gates arefurther moved to their extreme outward positions so that the webs 74,.75, come respectively into contact with stops 82 and 83, which are thepositions of maximum turbine power in the reverse direction, the forwardrotor blades 37, 38, will still be closed the blank annuli 72, 73, but.'.-.the reverse blades 37", 38, will be uncovered by the inner ends ofthose annuli and will be 0 en to admit fluid through the bars 78, $9respectively and to discharge fluid into the vanes and 36 through thebars 7 81, 79", respectively. This last position 'of the gate 72 isshown in Fig. 18, which is drawn on an enlarged scale.

As indicated in Figs. 16 and 17 the 'forward turbine-guide vanes 35, 36,and forward rotor-blades 37, 38", are of similar form to the blades 5and 6 respectively shown in Figs. 2, 6 and 9, except thatthe outlet endsof the rotor blades are for convenience of construction directedradially tion of the fluid entering them from the 25 helices 33 and 34.The reverse motor blades 37?, 38", will be variously designed accordingto principles well understood, and as already set forth in connectionwith Figs. 8 to 11, tosuit the conditions of fluid flow, according asthe secondary, or turbine shafts, arerequired to revolve in the' reversedirection at high velocities or, as usual in motor vehicles,

the reverse velocity is intended to be at all times low.

The reverse rotor-blades 35, 36, are formed to suit the vanes, 35!, 36",which discharge into them, but their outlet ends are preferablyapproximately tangential to axial planes, so that they discharge thefluid into the return chamber without bodily rotation.

The case 1, may be fitted with a branch opening 95, Fig. 15, preferablyleading from the helix 4, aS shown, in a direction approximatelytangential to the periphery of the pump rotor 2 for furnishing a supplyof fluid under pressure for auxiliary pur oses, as for instance to driveauxiliary tur ines generating electric light,. or for operatingself-starting apparatus and the like.

Fluid may be drawn from the casing 1 by the same branch 95, orotherwise, and circulated through a radiator or cooler of usual type inorder to dissipate the heat generated by fluid friction in the hydraulicapparatus, being returned to the casing 1, at a branch opening 96,leading into the return-chamber 65. Other branch openings may be formedin the case 1, such as the orifices 97 and 98 for respectively fillingand emptying it; the orifice 99 into which a Pitot-tube may be inserted,being connected with a pressure gage so as to determine the total energyof the fluid discharged from the pump; and the orifice 100 opposite theperiphery oil the pump rotor, which may be utilized forpurpe'ses-of'speed regulation as follows ':As already explained thespeed of the turbine shafts can be controlled at will by thejurbinegates while the engine and pumpi rotor are driven at constantspeed, the engine being governed by a centrifugal governor of any usualtype. In this case,

as also already explained,-'the fluid pressure generated by the pumpwill vary with the flow as controlled by the gates. Alternatively theengine governor may be replaced, in ways well understood, by a con stantrpressure governor, connected tothe orifice" .100 in sucha manner as tomaintain constant the pressure generated at the branch 100, z'. e. atthe periphery of the pump rotor 2, the result being thatwhen the-turbinegatesa're opened up so that the circulation of 'fluid is increased, thespeed of the engine automatically rises so as tomaintain the pressure.By this arrangement the engine is automaticallyaccelerated at the timesof maximum demand for power.

On the; other [hand when theiturbine-gate openin are' closed, with aconsequent tendency o the fluid pressure to increase due to the reducedflow, the hydraulic governor automatically reduces the engine speed soas to maintain such pressure constant, and thus gine at times whenlittle or no power is re uired from the secondary system.

order. to compensfite for loss of fluid from the system by lea age orevaporation, the casing" I'may be connected, as by a branch pipe fromthe orifice 96, to a reservoir fixed at such a level as to automaticallysupply such loss by gravitation and keep the casing filled.Alternatively such supply reservoir may be maintained at sufficientpressure to, supply such loss, by meansof compressedair stored above thefluid, m a manner well understood.

We claim y r 1. In hydraulic transmission mechanism of the type havingas driving element an outward flow centrifugal pump and as drivenelement an inward flowreaction tur"- bine, helical chamberssubstantially as described surrounding the (pump and turbine elementsrespectively an connected mouth to mouth, as and for the purposes setforth.

2. 'In hydraulic transmission mechanism an outward flow pump rotordischarging the circulated fluid into two peripheral helical chamberseach surrounding substantially one half of the periphery of such rotor,and

reduces the powerlost in the pump and endischarged from one of suchchambers into a peripheral helical chamber, the helical 3 chambersdischarging and .receiving each such portion of the circulated 'fluidbeing connected mouth to mouth, substantiallyas described. Y

4. In hydraulic transmission mechanism of the type specified, adoublexturbine rotor with a corresponding doubleperipheral series ofnon-rotatable guide-vanes surrounding it, one section of suchguide-vanes being arranged to co-act with one section of such rotor toproduce forward rotation, and the other pair of such sections beingarranged to co-act to produce reverse rotation, with means for closingthe outlets of either the forward guide-vanes, or the reverse guidevanes, or both together, at will, substantially as described.

5. In hydraulic transmission mechanism of the type specified, thecombination, with two turbine elements, of double turbinerotors with adouble peripheral series of guide-vanesin each such element, one sectionof the rotor and one section of such series of guide-vanesin each suchelement being arranged for forward rotation, and

the other pair of such sections in each such element being arranged forreverse rota- .tion, .with means for closing the outlets of either thefOIWuI'd guide-vanes, or the reverse guide-vanes, or both together, atwill.

6. In hydraulic transmission mechanism of the type specified, thecombination, with .an outward flow centrifugal pump, and one or moreperipheral helical chambers into which said pump discharges thecirculated -fluid, of guide blades arranged at the pc- .riphery iliariesto such helical chambers in directing the flow of the fluid,substantially as described.

7. In hydraulic transmission mechanism of the type specified, thecombination, with turbine rotors fitted with blades for alterof therotor of such pump as aux native forward and reverse rotation, ofmovable cylinder-gates having blank portions arranged to surround theinlet and outlet edges of the reverse blades when the forward blades arein operation, substantially as and for the purpose described.

8. In hydraulic transmission mechanism, the combination, a pump element,of a helical chamber surrounding each of said elements, said chamwith aturbine element and bers being connected mouth to mouth; and

separate peripheral series of forward and reverse guide-vanessurrounding the tur bine element and interposed between that element andits helical chamber, the latter inclosing both series of guide-vanes andsupplying fiuid thereto.

10. In hydraulic transmission mechanism, the combination of adouble-entry, centrifugal pump rotor; a pair of turbine rotors havingtheir axes arranged at opposite sides of and substantially parallel withthe axis of the pump rotor; a pair of helical chambers each of whichsurrounds one half of the periphery of said pump rotor; and a helicalchamber surrounding each turbine element, each of the last-namedchambers being connected mouth to mouth with the adjacent first-named,chamber. I

' In testimony whereof. we have hereunto set our hands in presence oftwo subscribing witnesses.

ANTHONY GEORGE MALDON MIGHELL. HENRY OhEMENT NEWTON. Witnesses:

EDWARD WATERS, EDWARD N. WATERS.

